Multi-control valve

Abstract

To provide a multi-control valve that can easily form a passage, and can be formed compactly.SOLUTION: A multi-control valve comprises: a first spool group including a spool for a bucket, a spool for an arm, a spool for a boom, a first traveling spool, a second traveling spool, and a turning spool; a valve block, on which a cargo side passage and a travel side passage are formed and through which each spool of the first spool group is inserted; and a second spool group including a regenerating spool and a cargo priority spool for priority-flowing liquid to the cargo side passage, each spool being inserted in the valve block in parallel to each spool of the first spool group. Each spool of the first spool group is arranged in line on the valve block in a predetermined direction, and each spool of the second spool group is arranged in line on the valve block in a predetermined direction, and to form a line different from each spool of the first spool group.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a multi-control valve into which a plurality of spools are inserted. [Background technology]

[0002] Construction machines such as excavators are equipped with a multi-control valve that controls the flow of hydraulic fluid to each actuator. One example of a multi-control valve is the hydraulic control valve device disclosed in Patent Document 1. In the hydraulic control valve device, spools that control the flow of hydraulic fluid to each actuator, i.e., drive system spools, are arranged in a row on the main body block. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 11-190044 Summary of the Invention [Problem to be solved by the invention]

[0004] In addition to the drive system spool, the multi-control valve is equipped with an auxiliary system spool. The auxiliary system spool is a spool that is installed in the multi-control valve in response to various requests such as energy saving and improved operability in construction machines. Examples of auxiliary system spools include a regeneration spool, a priority spool, and an unload spool. The auxiliary system spool is connected to a specific spool. Therefore, depending on the position where the auxiliary system spool is located, the passages formed in the multi-control valve become complex.

[0005] SUMMARY OF THE PRESENT EMBODIMENT An object of the present invention is to provide a multi-control valve which allows passages to be easily formed and which can be formed compactly. [Means for solving the problem]

[0006] The multi-control valve of the present disclosure includes a first spool group including a bucket spool that controls the flow of hydraulic fluid supplied to a bucket cylinder, an arm spool that controls the flow of hydraulic fluid supplied to an arm cylinder, a boom spool that controls the flow of hydraulic fluid supplied to a boom cylinder, a first traveling spool that controls the flow of hydraulic fluid supplied to a first traveling motor, a second traveling spool that controls the flow of hydraulic fluid supplied to a second traveling motor, and a swing spool that controls the flow of hydraulic fluid supplied to a swing motor; a loading side passage to which the bucket spool, the arm spool, the boom spool, and the swing spool are connected, and a traveling side passage to which the first traveling spool and the second traveling spool are connected, the second spool group includes a valve block through which each spool of a first spool group is inserted in parallel to each other, a regeneration spool that controls the flow of hydraulic fluid supplied from the rod side port to the head side port of the arm cylinder, and a loading / unloading priority spool that controls the flow rate of hydraulic fluid flowing in the travel side passage to preferentially flow hydraulic fluid to the loading side passage, wherein each spool of the first spool group is inserted into the valve block so as to be parallel to each other, and each spool of the first spool group is arranged in a row in a predetermined direction in the valve block, and each spool of the second spool group is arranged in a row in a predetermined direction in the valve block and to form a row different from each other with respect to each spool of the first spool group.

[0007] According to the present disclosure, the spools of the drive system that drive the actuators, i.e., the cylinders and the motors, are arranged in a row, which makes it easy to form the passages. Also, the spools of the auxiliary systems other than the drive system spools are arranged in a row next to the row of the drive system spools, which makes it possible to form a compact multi-control valve. Therefore, it is possible to improve the mountability on the equipment. Effect of the Invention

[0008] According to the present disclosure, the passage can be easily formed and can be formed compactly. [Brief description of the drawings]

[0009] [Figure 1] FIG. 1 is a plan view showing a multi-control valve according to an embodiment of the present disclosure. [Diagram 2] FIG. 2 is a circuit diagram showing a hydraulic circuit configured in the multi-control valve of FIG. [Diagram 3] 3 is a cross-sectional view of the multi-control valve of FIG. 1 taken along line III-III. [Figure 4] 4 is a cross-sectional view of the multi-control valve of FIG. 1 taken along line IV-IV. [Diagram 5] FIG. 2 is a bottom view showing the multi-control valve of FIG. 1. [Figure 6] 6 is a cross-sectional view of the multi-control valve of FIG. 1 taken along line VI-VI. [Figure 7] 7 is a cross-sectional view of the multi-control valve of FIG. 6 taken along line VII-VII. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] Hereinafter, the multi-control valve 1 according to the embodiment of the present disclosure will be described with reference to the drawings described above. The concept of direction used in the following description is used for convenience in the description and does not limit the orientation of the configuration of the present invention to that direction. Furthermore, the multi-control valve 1 described below is merely one embodiment of the present disclosure. Therefore, the present disclosure is not limited to the embodiment, and additions, deletions, and modifications are possible within the scope of the invention.

[0011] <Multi-control valve> A multi-control valve 1 as shown in FIG. 1 is provided in a construction machine such as a shovel. The construction machine is provided with hydraulic cylinders and hydraulic motors. In this embodiment, the construction machine is provided with hydraulic cylinders such as a bucket cylinder 2, an arm cylinder 3, and a boom cylinder 4, and hydraulic motors such as a first traveling motor 5, a second traveling motor 6, and a swing motor 7, as shown in FIG. 2. The construction machine is further provided with an option actuator (e.g., an option cylinder) 8. The bucket cylinder 2, the arm cylinder 3, and the boom cylinder 4 respectively operate the bucket, the arm, and the boom (all not shown). The first traveling motor 5 and the second traveling motor 6 respectively operate each of a pair of crawlers. The option cylinder 8 operates, for example, a breaker and a nipper.

[0012] The multi-control valve 1 is connected to a plurality of actuators 2-8. The multi-control valve 1 controls the flow of hydraulic fluid supplied to and discharged from the plurality of actuators 2-8. In this embodiment, the multi-control valve 1 is a one-pump system multi-control valve having one pump port 35, as will be described later. The multi-control valve 1 mainly includes a valve block 11, a first spool group 12, and a second spool group 13.

[0013] The valve block 11 has various passages 21a to 27a, 21b to 27b, 32, 33, 34, and 36 and ports 35 and 36a, which will be described in detail later. The valve block 11 is formed, for example, in a rectangular parallelepiped shape as shown in FIG. 1. The valve block 11 is formed in a rectangular shape in a plan view seen from one side in the height direction. A pump port 35 and a tank port 36a shown in FIG. 2 are formed on a side surface (i.e., one side surface) on one side in the short side direction of the valve block 11. A hydraulic pump 16 and a tank 17 are connected to each of the ports 35 and 36a. In addition, a plurality of actuator ports (not shown) are formed on a side surface (i.e., the other side surface) on the other side in the short side direction of the valve block 11. A plurality of actuators 2 to 8 are connected to each of the actuator ports.

[0014] The first spool group 12 includes a plurality of drive system spools 21-27 as shown in Fig. 1. More specifically, the first spool group 12 includes a first traveling spool 21, a second traveling spool 22, a bucket spool 23, an arm spool 24, a boom spool 25, a swing spool 26, and an option spool 27. On the other hand, the second spool group 13 includes a plurality of auxiliary system spools 28, 29, and a valve body 30. More specifically, the second spool group 13 includes a loading priority spool with an unloading function (hereinafter simply referred to as a "loading priority spool") 28, an arm regeneration spool 29, and a pressure compensation valve body 30.

[0015] Each of the spools 21-29 and the valve element 30 is slidably inserted into the valve block 11. The spools 21-27 of the drive system control the flow of hydraulic fluid to each of the actuators 2-8 by changing their positions. On the other hand, the spools 28, 29 and the pressure compensation valve element 30 of the auxiliary system achieve various functions (regeneration function, loading priority function, unloading function, and pressure retention function) by changing their positions.

[0016] 1 and 3, the multi-control valve 1 includes a plurality of solenoid valves 14a to 14r and a plurality of relief valves 15a to 15h. Each of the solenoid valves 14a to 14r is provided in the valve block 11 in correspondence with each of the spools 21 to 29. Each of the solenoid valves 14a to 14r outputs a pilot pressure to the corresponding spool 21 to 29 in response to an input signal. As a result, each of the solenoid valves 14a to 14r changes the position of the corresponding spool 21 to 29, that is, strokes the corresponding spool 21 to 29. The plurality of solenoid valves 14a to 14r constitute two solenoid valve groups 14A and 14B, as will be described later in detail.

[0017] Each of the relief valves 15a-15h shown in Figures 1, 4, and 5 is provided in the valve block 11 corresponding to some of the spools 23-25, 27 of the drive system spools 21-27. Each of the relief valves 15a-15h discharges the hydraulic fluid to the tank 17 when the hydraulic fluid supplied from the corresponding spools 23-25, 27 to the actuators 2-4, 8 reaches or exceeds a predetermined relief pressure. The relief valves 15a-15h respectively constitute a first relief valve group 15A and a second relief valve group 15B, as will be described in detail later.

[0018] <Hydraulic circuit in multi-control valve> The hydraulic circuit 9 in the multi-control valve 1 will be described below with reference to Fig. 2. In the valve block 11, various passages are formed, mainly a cargo-handling side passage 32, a travel-side passage 33, and a communication passage 34. The cargo-handling side passage 32 is connected to a pump port 35. A hydraulic pump 16 that discharges hydraulic fluid is connected to the pump port 35. The cargo-handling side passage 32 is connected to the cargo-handling side passage 32 so that the cargo-handling system spools 23-27 among the drive system spools 21-27 are arranged in parallel. The cargo-handling system spools 23-27 are spools that control the hydraulic fluid flowing to the cargo-handling system actuators 2-4, 7, and 8. In this embodiment, the cargo-handling system actuators 2-4, 7, and 8 are the bucket cylinder 2, the arm cylinder 3, the boom cylinder 4, the swing motor 7, and the option cylinder 8. That is, the cargo handling spools 23 to 27 include a bucket spool 23, an arm spool 24, a boom spool 25, a rotation spool 26, and an option spool 27.

[0019] The bucket spool 23 controls the flow of the hydraulic fluid supplied to the bucket cylinder 2. More specifically, the bucket spool 23 is connected to the loading-side passage 32 and the tank passage 36. The tank passage 36 extends in the longitudinal direction in the valve block 11 and is formed throughout the valve block 11 (see FIG. 3, which will be described later in detail). The tank passage 36 is connected to the tank 17 via a tank port 36a as shown in FIG. 2. Furthermore, the bucket spool 23 is connected to the head-side port 2a of the bucket cylinder 2 via a head-side passage 23a, and is connected to the rod-side port 2b of the bucket cylinder 2 via a rod-side passage 23b. The bucket spool 23 receives pilot pressures output from the solenoid valves 14e, 14f in opposing directions. The bucket spool 23 is biased by a spring mechanism 43 to resist the pilot pressures it receives. Therefore, the bucket spool 23 strokes to a position according to the pilot pressures of the solenoid valves 14e, 14f. The bucket spool 23 switches the connection between the loading side passage 32 and the tank passage 36 by stroking, and also adjusts the opening degree of the bucket spool 23. In this way, the bucket spool 23 controls the flow of hydraulic fluid to the head side port 2a and the rod side port 2b of the bucket cylinder 2.

[0020] The arm spool 24 controls the flow of hydraulic fluid supplied to the arm cylinder 3. More specifically, the arm spool 24 has a first spool member 24c and a second spool member 24d. The first spool member 24c and the second spool member 24d are connected to the loading side passage 32 and the tank passage 36, respectively. The first spool member 24c and the second spool member 24d are connected to the head side port 3a of the arm cylinder 3 via the head side passage 24a. The first spool member 24c is connected to the rod side port 3b via the rod side passage 24b. The first spool member 24c receives the pilot pressures output from the solenoid valves 14g and 14h in opposing directions. The second spool member 24d receives the pilot pressures output from the solenoid valves 14h and 14i in opposing directions. Furthermore, the first spool member 24c and the second spool member 24d are provided with spring mechanisms 44, 45 that apply a biasing force against the pilot pressure received. Therefore, the first spool member 24c strokes to a position corresponding to the pilot pressure of each solenoid valve 14g, 14h, and the second spool member 24d strokes to a position corresponding to the pilot pressure of each solenoid valve 14h, 14i. The first spool member 24c and the second spool member 24d stroke to switch the connection destination of the loading side passage 32 and the tank passage 36, and adjust the opening degree of each of the first spool member 24c and the second spool member 24d. As a result, the arm spool 24 controls the flow of hydraulic fluid to the head side port 3a and the rod side port 3b of the arm cylinder 3.

[0021] The boom spool 25 controls the flow of hydraulic fluid supplied to the boom cylinder 4. More specifically, the boom spool 25 has a first spool member 25c and a second spool member 25d. The first spool member 25c and the second spool member 25d are connected to the loading-side passage 32 and the tank passage 36, respectively. Furthermore, the first spool member 25c is connected to the rod-side port 4b via the rod-side passage 25b. The first spool member 25c also receives the pilot pressures output from the solenoid valves 14j and 14k in opposing directions. The second spool member 25d is connected to the head-side port 4a of the boom cylinder 4 via the head-side passage 25a. The second spool member 25d also receives the pilot pressures output from the solenoid valves 14k and 14l in opposing directions. Furthermore, the first spool member 25c and the second spool member 25d are provided with spring mechanisms 46, 47 that apply a biasing force against the pilot pressure received. Therefore, the first spool member 25c strokes to a position corresponding to the pilot pressure of each solenoid valve 14j, 14k, and the second spool member 25d strokes to a position corresponding to the pilot pressure of each solenoid valve 14k, 14l. The first spool member 25c and the second spool member 25d stroke to switch the connection destination of the loading side passage 32 and the tank passage 36, and adjust the opening degree of each of the first spool member 25c and the second spool member 25d. As a result, the boom spool 25 controls the flow of hydraulic fluid to the head side port 4a and the rod side port 4b of the boom cylinder 4.

[0022] The swing spool 26 controls the flow of hydraulic fluid supplied to the swing motor 7. More specifically, the swing spool 26 is connected to the cargo-side passage 32 and the tank passage 36. Furthermore, the swing spool 26 is connected to the first supply / discharge port 7a and the second supply / discharge port 7b of the swing motor 7 through the supply / discharge passages 26a and 26b, respectively. The swing spool 26 receives pilot pressures output from the solenoid valves 14m and 14n in opposing directions. The swing spool 26 is biased by the spring mechanism 48 to resist the pilot pressures it receives. Therefore, the swing spool 26 strokes to a position according to the pilot pressures of the solenoid valves 14m and 14n. The swing spool 26 strokes to switch the connection destination between the cargo-side passage 32 and the tank passage 36 and adjust the opening degree of the swing spool 26. As a result, the swing spool 26 controls the flow of hydraulic fluid to the first supply / discharge port 7a and the second supply / discharge port 7b of the swing motor 7.

[0023] The option spool 27 controls the flow of hydraulic fluid supplied to the option cylinder 8. More specifically, the option spool 27 is connected to the cargo-side passage 32 and the tank passage 36. Furthermore, the option spool 27 is connected to the head-side port 8a of the option cylinder 8 via the head-side passage 27a, and to the rod-side port 8b via the rod-side passage 27b. The option spool 27 receives the pilot pressures output from the solenoid valves 14o and 14p in opposing directions. The option spool 27 is also biased by a spring mechanism 49 to resist the pilot pressures it receives. Therefore, the option spool 27 strokes to a position according to the pilot pressures of the solenoid valves 14o and 14p. The option spool 27 strokes to switch the connection destination between the cargo-side passage 32 and the tank passage 36, and adjusts the opening of the option spool 27. As a result, the option spool 27 controls the flow of hydraulic fluid to the head side port 8a and the rod side port 8b of the option cylinder 8.

[0024] The travel-side passage 33 is connected to the loading-side passage 32 via the loading-side priority spool 28, which will be described later in detail. The hydraulic fluid of the hydraulic pump 16 is guided to the travel-side passage 33 via the loading-side priority spool 28. In addition, the travel-side passage 33 is connected to the travel-side spools 21 and 22, among the drive system spools 21 to 27, so that they are arranged in parallel. The travel-side spools 21 and 22 are spools that control the hydraulic fluid supplied to the travel-system actuators 5 and 6, which are the first travel motor 5 and the second travel motor 6.

[0025] The first traveling spool 21, which is one of the traveling system spools 21, controls the flow of hydraulic fluid supplied to the first traveling motor 5. More specifically, the first traveling spool 21 is connected to the traveling side passage 33 and the tank passage 36. The first traveling spool 21 is connected to the first supply / exhaust port 5a and the second supply / exhaust port 5b of the first traveling motor 5 through the supply / exhaust passages 21a and 21b, respectively. The first traveling spool 21 receives pilot pressures output from the solenoid valves 14a and 14b in opposing directions. The first traveling spool 21 is also biased by the spring mechanism 41 to resist the pilot pressures it receives. Therefore, the first traveling spool 21 strokes to a position according to the pilot pressures of the solenoid valves 14a and 14b. The first traveling spool 21 strokes to switch the connection destination between the traveling side passage 33 and the tank passage 36, and adjusts the opening degree of the first traveling spool 21. As a result, the first traveling spool 21 controls the flow of hydraulic fluid to the first supply / discharge port 5a and the second supply / discharge port 5b of the first traveling motor 5.

[0026] The second traveling spool 22, which is the other traveling system spool 22, controls the flow of the hydraulic fluid supplied to the second traveling motor 6. More specifically, the second traveling spool 22 is connected to the traveling side passage 33 and the tank passage 36. The second traveling spool 22 is connected to the first supply / discharge port 6a and the second supply / discharge port 6b of the second traveling motor 6 through the supply / discharge passages 22a and 22b, respectively. The second traveling spool 22 receives the pilot pressures output from the solenoid valves 14c and 14d in opposing directions. The second traveling spool 22 is also biased by the spring mechanism 42 to resist the pilot pressures it receives. Therefore, the second traveling spool 22 strokes to a position according to the pilot pressures of the solenoid valves 14c and 14d. The second traveling spool 22 switches the connection destination between the traveling side passage 33 and the tank passage 36 by stroking, and the opening degree of the second traveling spool 22 is adjusted to the opening degree. As a result, the second traveling spool 22 controls the flow of hydraulic fluid to the first supply / discharge port 6a and the second supply / discharge port 6b of the second traveling motor 6.

[0027] The communication passage 34 is connected to the first traveling spool 21 and the second traveling spool 22. The communication passage 34 communicates the first traveling motor 5 and the second traveling motor 6 when the hydraulic fluid is supplied to the first traveling motor 5 and the second traveling motor 6. More specifically, when the first traveling spool 21 strokes, the communication passage 34 is connected to the supply and discharge passages 21a and 21b connecting the first traveling motor 5 and the traveling side passage 33. When the second traveling spool 22 strokes, the communication passage 34 is connected to the supply and discharge passages 22a and 22b connecting the second traveling motor 6 and the traveling side passage 33. This prevents the flow rate of hydraulic fluid supplied to the two traveling motors 5 and 6 from being biased when the first traveling motor 5 and the second traveling motor 6 are simultaneously operated during straight traveling. This improves the straight traveling ability of the construction machine.

[0028] The cargo-loading priority spool 28 controls the flow rate of the hydraulic fluid flowing through the travel-side passage 33, thereby preferentially flowing the hydraulic fluid through the cargo-loading side passage 32. More specifically, the cargo-loading priority spool 28 is connected to the cargo-loading side passage 32 and the travel-side passage 33. The cargo-loading priority spool 28 receives pilot pressure from the solenoid valve 14q. Furthermore, the cargo-loading priority spool 28 is biased by the spring mechanism 50 against the pilot pressure it receives. Therefore, the cargo-loading priority spool 28 strokes to a position according to the pilot pressure of each solenoid valve 14q, and the opening degree of the cargo-loading priority spool 28 is adjusted. As a result, the cargo-loading priority spool 28 controls the flow rate of the hydraulic fluid flowing through the travel-side passage 33, thereby preferentially flowing the hydraulic fluid through the cargo-loading side passage 32.

[0029] The cargo-loading priority spool 28 also has an unloading function. More specifically, the cargo-loading priority spool 28 can move to an unloading position A1. At the unloading position A1, the hydraulic fluid flowing through the cargo-loading passage 32 is discharged. More specifically, the cargo-loading priority spool 28 is also connected to the tank passage 36. The cargo-loading priority spool 28 is located at the unloading position A1 when the pilot pressure from the solenoid valve 14q is smaller than a predetermined pressure. At the unloading position A1, the cargo-loading priority spool 28 connects the cargo-loading passage 32 to the travel-side passage 33 and the tank passage 36. This connects the cargo-loading passage 32 to the tank passage 36, and the hydraulic pump 16 is in an unloaded state.

[0030] In addition, when the pilot pressure from the solenoid valve 14q becomes equal to or higher than a predetermined pressure, the cargo-unloading priority spool 28 is located at the travel position A2 or the priority position A3. In the travel position A2 and the priority position A3, the cargo-unloading side passage 32 is connected to the travel-side passage 33. Then, the hydraulic fluid flowing through the cargo-unloading side passage 32 is led to the travel-side passage 33. On the other hand, the cargo-unloading side passage 32 is disconnected from the tank passage 36. In the travel position A2, the opening degree of the cargo-unloading priority spool 28 is maximum (including full opening). In the priority position A3, the opening degree of the cargo-unloading priority spool 28 (i.e., the opening degree between the cargo-unloading side passage 32 and the travel-side passage 33) is adjusted according to the position according to the pilot pressure of each solenoid valve 14q. That is, in the priority position A3, the opening degree of the cargo-unloading priority spool 28 is narrowed according to the stroke amount of the cargo-unloading priority spool 28.

[0031] The arm regeneration spool 29 controls the flow of hydraulic fluid supplied from the rod side port 3b to the head side port 3a of the arm cylinder 3. That is, the arm regeneration spool 29 regenerates the hydraulic fluid discharged from the rod side port 3b to the head side port 3a. More specifically, the arm regeneration spool 29 is connected to the head side passage 24a and the rod side passage 24b that are connected to the arm cylinder 3. The arm regeneration spool 29 receives pilot pressure from the solenoid valve 14r. Furthermore, the arm regeneration spool 29 is biased by the spring mechanism 51 so as to resist the pilot pressure it receives. Therefore, the arm regeneration spool 29 communicates between the head side passage 24a and the rod side passage 24b in response to the pilot pressure of each solenoid valve 14r. As a result, the arm regeneration spool 29 can regenerate the hydraulic fluid discharged from the rod side port 3b to the head side port 3a.

[0032] The pressure compensating valve element 30 maintains the pressure in the loading / unloading passage 32 by discharging the hydraulic fluid. More specifically, the pressure compensating valve element 30 is connected to the loading / unloading passage 32. The pressure compensating valve element 30 connects the loading / unloading passage 32 and the tank passage 36 in accordance with the pressure in the loading / unloading passage 32.

[0033] The relief valves 15a to 15h are provided corresponding to the cylinders 2 to 4, 8. The relief valves 15a to 15h discharge the hydraulic fluid to the tank 17 when the pressure of the hydraulic fluid supplied to the corresponding cylinders 2 to 4, 8 exceeds a predetermined relief pressure. More specifically, the relief valves 15a, 15c, 15e, 15g are connected to the head side passages 23a to 25a, 27a, respectively. The relief valves 15b, 15d, 15f, 15h are connected to the rod side passages 23b to 25b, 27b, respectively. Furthermore, each of the relief valves 15a to 15h is connected to the tank passage 36. Each of the relief valves 15a to 15h discharges the hydraulic fluid to the tank 17 when the pressure of the passages 23a to 25a, 27a, 23b to 25b, 27b connected thereto exceeds a predetermined relief pressure.

[0034] <Flow of hydraulic fluid in a multi-control valve> The multi-control valve 1 operates as follows when the traveling actuators 5, 6 are driven. That is, when pilot pressure is output from any one of the solenoid valves 14a to 14d, the corresponding traveling spools 21, 22 are actuated. At this time, the loading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q. For example, when pilot pressure is output from the solenoid valves 14a, 14c, the loading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q and the traveling spools 21, 22 are actuated. As a result, the hydraulic fluid from the hydraulic pump 16 is supplied to each traveling motor 5, 6. Then, each traveling motor 5, 6 rotates in a direction to move the construction machine forward. At this time, the two traveling motors 5, 6 are communicated with each other by the communication passage 34. As a result, the bias in the flow rate of the hydraulic fluid supplied to the two traveling motors 5, 6 is suppressed, so that the straightness of the construction machine can be improved.

[0035] In addition, when the loading / unloading actuators 2-4, 7, and 8 are driven, they operate as follows. That is, when pilot pressure is output from any of the solenoid valves 14e-14n, the corresponding spools 23-27 are actuated. At this time, the loading priority spool 28 moves to the travel position A2 by the pilot pressure from the solenoid valve 14q. For example, when pilot pressure is output from the solenoid valve 14e, the bucket spool 23 is actuated. At the same time, the loading priority spool 28 moves to the travel position A2 by the pilot pressure from the solenoid valve 14q, and the opening of the loading priority spool 28 is adjusted to the minimum opening (including fully closed). Then, the hydraulic fluid from the hydraulic pump 16 is preferentially supplied to the head side port 2a of the bucket cylinder 2, and the hydraulic fluid is pushed out from the rod side port 2b and discharged into the tank 17. As a result, the bucket cylinder 2 extends.

[0036] Furthermore, when pilot pressure is output from the solenoid valves 14g and 14i, the arm spool 24 is actuated. At the same time, the loading priority spool 28 is moved to the travel position A2 by the pilot pressure from the solenoid valve 14q, and the opening of the loading priority spool 28 is adjusted to the minimum opening (including fully closed). Then, the hydraulic fluid from the hydraulic pump 16 is supplied to the head side port 3a of the arm cylinder 3, and the hydraulic fluid is pushed out from the rod side port 2b. At this time, the arm regeneration spool 29 is actuated, and the hydraulic fluid pushed out from the rod side port 2b is regenerated to the head side port 3a.

[0037] Furthermore, when the traveling actuators 5, 6 and the loading actuators 2-4, 7, 8 are operated simultaneously, they operate as follows. That is, when pilot pressure is output from any of the solenoid valves 14a-14d and pilot pressure is output from any of the solenoid valves 14e-14n, the corresponding spools 21-27 are operated. At this time, the loading priority spool 28 moves to the priority position A3 by the pilot pressure from the solenoid valve 14q. Then, pilot pressure according to the pilot pressure of each of the solenoid valves 14a-14n is output from the solenoid valve 14q to adjust the opening degree of the loading priority spool 28. More specifically, the opening degree of the loading priority spool 28 is adjusted according to the operation amount of each of the actuators 2-8 (more specifically, the opening degree is narrowed). As a result, the flow rate of the hydraulic fluid flowing through the traveling side passage 33 is restricted, and the hydraulic fluid flows preferentially through the loading side passage 32. That is, when the traveling actuators 5, 6 and the cargo-handling actuators 2-4, 7, 8 are operated simultaneously, the hydraulic fluid can be made to flow preferentially to the cargo-handling actuators 2-4, 7, 8.

[0038] Furthermore, when the traveling system actuators 5, 6 and the cargo-unloading system actuators 2-4, 7, 8 are not being operated, the multi-control valve 1 operates as follows. That is, the cargo-unloading priority spool 28 is located at the unloading position A1. As a result, the cargo-unloading side passage 32 is connected to the tank 17 via the cargo-unloading priority spool 28. This allows the hydraulic pump 16 to be in the unloading state.

[0039] <Specific configuration of the multi-control valve> The specific configuration of the multi-control valve 1 will be described below. As described above, the valve block 11 of the multi-control valve 1 is formed, for example, in a substantially rectangular parallelepiped shape. To explain in more detail, the valve block 11 includes a block body 11a, a first solenoid valve block 11b, and a second solenoid valve block 11c (see Figs. 1 and 5). The spools 21-29 of the first spool group 12 and the second spool group 13 and the pressure compensation valve element 30 are inserted into the valve block 11 (the block body 11a in this embodiment).

[0040] The block body 11a is formed, for example, in a substantially rectangular parallelepiped shape. The block body 11a is formed in a rectangular shape in a plan view from one side in the height direction. The spools 21-29 of the first spool group 12 and the second spool group 13 and the pressure compensation valve element 30 are inserted into the block body 11a as follows. That is, as shown in FIG. 1, the spools 21-27 of the first spool group 12 are aligned in a line in the longitudinal direction, which is an example of a predetermined direction, in a plan view, and are inserted into the block body 11a parallel to each other (see also FIG. 3). In FIG. 1, the spring mechanisms 41-44, 46, 48, 49 provided at one end of the axial direction (i.e., height direction) of each spool 21-27 are aligned in a line in the longitudinal direction. In this embodiment, the spools 21-27 of the first spool group 12 are arranged in the order of, for example, the arm spool 24, the first traveling spool 21, the swivel spool 26, the boom spool 25, the option spool 27, the second traveling spool 22, and the bucket spool 23 from one side in the longitudinal direction. Note that the order in which the spools 21-27 are arranged in the longitudinal direction is just an example, and the order may be different from that described above. In this embodiment, the spools 21-27 of the first spool group 12 are inserted into a central portion of the block body 11a in the lateral direction in a line.

[0041] The spools 28, 29 and the pressure compensating valve element 30 of the second spool group 13 are inserted into the block body 11a so as to be aligned in a line in the longitudinal direction, which is an example of a predetermined direction, in a plan view as shown in FIG. 1 (see also FIG. 4). The spools 28, 29 and the pressure compensating valve element 30 of the second spool group 13 are inserted into the block body 11a so as to be aligned in different rows from the spools 21 to 27 of the first spool group 12. To explain in more detail, the second spool group 13 is disposed on one side of the first spool group 12 in the lateral direction in the block body 11a as shown in FIG. 1. That is, the spools 28, 29 and the pressure compensating valve element 30 of the second spool group 13 are inserted into the block body 11a so as to be aligned in a row on one side of the spools 21 to 27 of the first spool group 12 in the lateral direction. In this embodiment, the spools 28, 29 and the pressure compensation valve element 30 are arranged, for example, from one side in the longitudinal direction in the order of the arm regeneration spool 29, the pressure compensation valve element 30, and the loading priority spool 28.

[0042] Furthermore, in the block body 11a, relief valves 15a to 15h are arranged as follows. That is, among the relief valves 15a to 15h, the relief valves 15b, 15d, 15e, and 15h constitute a first relief valve group 15A. Also, among the relief valves 15a to 15h, the rod-side relief valves 15a, 15c, 15f, and 15g constitute a second relief valve group 15B.

[0043] The first relief valve group 15A is arranged in a row on a main surface 11d on one side in the height direction of the block body 11a as shown in Fig. 1. The first relief valve group 15A is arranged in the block body 11a so as to form a row different from each of the first spool group 12 and the second spool group 13 in a plan view. To explain in more detail, the first relief valve group 15A is arranged on the other side of the first spool group 12 in the short side direction of the block body 11a as shown in Fig. 1. That is, the relief valves 15b, 15d, 15e, and 15h of the first relief valve group 15A are arranged in the block body 11a so as to form a row on the other side of the short side direction of the spools 21 to 27 of the first spool group 12.

[0044] On the other hand, the second relief valve group 15B is arranged side by side on one side and the other side in the lateral direction of a bottom surface 11f on the other side in the height direction of the block body 11a in the bottom view shown in Fig. 5. To explain in more detail, the relief valves 15a, 15c of the second relief valve group 15B are arranged apart from each other on both sides in the longitudinal direction on one side in the lateral direction of the bottom surface 11f. Moreover, the relief valves 15f, 15g are arranged in a longitudinal middle portion on the other side in the lateral direction of the bottom surface 11f. In this embodiment, the relief valves 15f, 15g are arranged between the relief valves 15a, 15c in a side view seen in the lateral direction.

[0045] The first solenoid valve block 11b is a block for mounting the first solenoid valve group 14A as shown in FIG. 1. The first solenoid valve group 14A includes a plurality of solenoid valves 14a, 14c, 14e, 14g, 14h, 14j, 14k, 14m, 14o, 14q, and 14r. The other solenoid valves 14b, 14d, 14f, 14i, 14l, 14n, and 14p form the second solenoid valve group 14B. The first solenoid valve block 11b is formed, for example, in a rectangular column shape extending in the longitudinal direction. The first solenoid valve block 11b is provided on one side surface on one side of the short side of the block main body 11a in the plan view shown in FIG. 1. In this embodiment, the first solenoid valve block 11b is attached to one side surface of the block main body 11a on one side in the height direction.

[0046] The first solenoid valve group 14A is arranged on a main surface 11e on one side in the height direction of the first solenoid valve block 11b. More specifically, in the first solenoid valve group 14A, a plurality of solenoid valves 14a, 14c, 14e, 14g, 14h, 14j, 14k, 14m, 14o, 14q, and 14r are arranged in a plurality of rows (two rows in this embodiment). Each row extends in the longitudinal direction. Therefore, the first solenoid valve group 14A is arranged in a plurality of rows in the longitudinal direction of the valve block 11, and is arranged to form a row different from the first spool group 12 and the second spool group 13.

[0047] The second solenoid valve block 11c shown in FIG. 5 is a block for mounting the second solenoid valve group 14B. The second solenoid valve block 11c is, for example, a long member extending in the longitudinal direction. The second solenoid valve block 11c is provided on the bottom surface 11f of the block main body 11a in a bottom view. More specifically, the second solenoid valve block 11c is attached to the bottom surface 11f of the block main body 11a at a middle portion in the short side direction. In this embodiment, the second solenoid valve block 11c is disposed so as to correspond to the first spool group 12 (more specifically, so as to overlap the first spool group 12 in a bottom view). The spring mechanisms 45, 47 of the arm spool 24 and the boom spool 25 protrude from the second solenoid valve block 11c to the other side in the height direction. As a result, in the second solenoid valve block 11c, the spring mechanisms 45, 47 of the arm spool 24 and the boom spool 25 are arranged in a row in the middle part in the short side direction. Also, the relief valves 15a, 15c, 15f, 15g of the second relief valve group 15B are arranged on one side and the other side in the short side direction, sandwiching the second solenoid valve block 11c therebetween.

[0048] The second solenoid valve group 14B is arranged in the second solenoid valve block 11c. In this embodiment, the solenoid valves 14b, 14d, 14f, 14i, 14l, 14n, and 14p of the second solenoid valve group 14B are arranged in a row in the intermediate portion in the short side direction together with the spring mechanisms 45 and 47 of the arm spool 24 and the boom spool 25.

[0049] In addition, the valve block 11 (block body 11a in this embodiment) has the passages 32, 33, and 34 formed as follows. That is, the loading side passage 32, the traveling side passage 33, and the communication passage 34 are formed between the first spool group 12 and the second spool group 13 in the short side direction (see the section line VV in FIG. 1 and FIG. 6). In addition, the loading side passage 32, the traveling side passage 33, and the communication passage 34 extend in the longitudinal direction as shown in FIG. 6. In more detail, the loading side passage 32, the traveling side passage 33, and the communication passage 34 penetrate the block body 11a from one end to the other end in the longitudinal direction. And, both ends of the loading side passage 32, the traveling side passage 33, and the communication passage 34 are respectively blocked by plugs 60 or plates 66. Furthermore, the passages 32, 33, and 34 are arranged in the order of the communication passage 34, the traveling side passage 33, and the loading side passage 32 from one side in the height direction. However, the order in which the passages 32, 33, and 34 are arranged is not limited to the order described above.

[0050] Furthermore, as shown in FIG. 7, the pump port 35 is formed on one side surface of the block body 11a as described above. In this embodiment, the pump port 35 is formed in a longitudinal intermediate portion. The pump port 35 is disposed adjacent to the priority loading spool 28 in the longitudinal direction. The pump port 35 is connected to the loading side passage 32. The loading side passage 32 is configured as follows in the valve block 11 (block body 11a in this embodiment). That is, the loading side passage 32 is connected to five branch passages 32a to 32e. The branch passages 32a to 32e are connected to the spools 23 to 27 via the check valves 61 to 65, respectively. The priority loading spool 28 is connected to the loading side passage 32 in a longitudinal intermediate portion (longitudinal center portion in this embodiment). 4, the loading-side passage 32 is connected to the traveling-side passage 33 and the tank passage 36 via the loading priority spool 28. Furthermore, a pressure compensation valve body 30 is connected to the loading-side passage 32 as shown in FIGS.

[0051] The travel-side passage 33 is also connected to a loading priority spool 28 at a longitudinal intermediate portion (in the present embodiment, the longitudinal center portion) as shown in FIG. 4. Furthermore, the first running spool 21 and the second running spool 22 are connected to the travel-side passage 33 as shown in FIG. 6. The first running spool 21 and the second running spool 22 are disposed apart from each other in the longitudinal direction in the travel-side passage 33. The loading priority spool 28 is disposed between the first running spool 21 and the second running spool 22 as viewed in the lateral direction as shown in FIG. 7. In the present embodiment, the loading priority spool 28 is disposed at a position equidistant from the first running spool 21 and the second running spool 22 as viewed in the lateral direction. However, the loading priority spool 28 is not limited to being disposed in such a position.

[0052] 6, the communication passage 34 is connected to the first traveling spool 21 and the second traveling spool 22 via branch passages 34a and 34b. The communication passage 34 is connected to the first traveling spool 21 and the second traveling spool 22 without spanning the spools 23 to 29.

[0053] Furthermore, the block body 11a has openings of the passages 21a to 27a and 21b to 27b (i.e., the actuator ports described above) formed on the other side surface (not shown) that are connected to the spools 21 to 27. The actuators 2 to 8 are connected to the openings of the passages 21a to 27a and 21b to 27b.

[0054] In the multi-control valve 1 of this embodiment, the spools 21-26 of the drive system that drive the actuators 2-8 are arranged in a row, which makes it easy to form the passages 32-34. Also, the spools 28, 29 of the auxiliary system other than the spools 21-26 of the drive system are arranged in a row next to the row of the spools 21-26 of the drive system, which makes it possible to form the multi-control valve 1 compact. This improves the ease of mounting on construction machinery and the like.

[0055] In the multi-control valve 1 of this embodiment, the cargo-unloading priority spool 28 can be moved to an unloading position A1 and a priority position A3. In addition, the cargo-unloading priority spool 28 discharges the hydraulic fluid flowing through the cargo-unloading side passage 32 at the unloading position A1. In addition, the cargo-unloading priority spool 28 preferentially causes the hydraulic fluid to flow through the cargo-unloading side passage 32 at the priority position A3. Therefore, the cargo-unloading priority spool 28 has an unloading function and a cargo-unloading priority function. Therefore, the unloading spool can be omitted in the multi-control valve 1. This allows the number of parts in the multi-control valve 1 to be reduced.

[0056] Furthermore, in the multi-control valve 1 of this embodiment, the loading / unloading priority spool 28 is disposed between the first traveling spool 21 and the second traveling spool 22 when viewed in the column direction. Therefore, the difference in the length of the passage from the loading / unloading priority spool 28 to each traveling spool 21, 22 can be reduced. That is, the difference in the passage pressure loss from the loading / unloading priority spool to each traveling spool can be reduced. In this embodiment, the loading / unloading priority spool 28 is disposed at an equal distance from each traveling spool 21, 22, so that the passage pressure loss from the loading / unloading priority spool 28 to each traveling spool 21, 22 can be made substantially the same.

[0057] Furthermore, in the multi-control valve 1 of this embodiment, the pump port 35 is connected to the cargo-side passage 32. Therefore, the length of the passage from the pump port 35 to each of the spools 23-27 of the cargo-handling system can be reduced. This makes it possible to suppress the pressure loss in the passage from the pump port 35 to each of the spools 23-27 of the cargo-handling system.

[0058] Furthermore, in the multi-control valve 1 of this embodiment, the travel-side passage 33 is connected to the loading-side passage 32 via the loading priority spool 28. Therefore, the passage connecting the pump port 35 and the loading-side passage 32 can be omitted. This makes it possible to reduce the number of passages formed in the valve block 11.

[0059] <Other embodiments> The spools 21-29 included in each of the first spool group 12 and the second spool group 13 of the multi-control valve 1 of this embodiment are merely examples, and other spools and valve bodies may be included. The order in which the spools 21-29 and the pressure compensation valve body 30 are arranged in each of the first spool group 12 and the second spool group 13 is not limited to the order described above, and any order may be used. In the multi-control valve 1 of this embodiment, the row direction in which the first spool group 12 and the second spool group 13 are arranged is the short side direction, but it may also be the height direction. The solenoid valves 14a-14r are not necessarily arranged as described above, and may be arranged on both sides of the first spool group 12 and the second spool group 13 in the short side direction.

[0060] In the multi-control valve 1 of this embodiment, the valve block 11 includes the block body 11a, the first solenoid valve block 11b, and the second solenoid valve block 11c, but they may be integrally configured. In the valve block 11 of this embodiment, the loading side passage 32, the traveling side passage 33, and the communication passage 34 are arranged between the first spool group 12 and the second spool group 13 in the short side direction, but they do not have to be arranged in this manner. For example, at least one of the traveling side passage 33, the communication passage 34, and the loading side passage 32 may be formed on the other short side of the first spool group 12. In addition, at least one of the traveling side passage 33, the communication passage 34, and the loading side passage 32 does not have to extend to one or the other end in the longitudinal direction.

[0061] Exemplary embodiments A multi-control valve in a first aspect includes a first spool group including a bucket spool for controlling a flow of hydraulic fluid supplied to a bucket cylinder, an arm spool for controlling a flow of hydraulic fluid supplied to an arm cylinder, a boom spool for controlling a flow of hydraulic fluid supplied to a boom cylinder, a first traveling spool for controlling a flow of hydraulic fluid supplied to a first traveling motor, a second traveling spool for controlling a flow of hydraulic fluid supplied to a second traveling motor, and a swing spool for controlling a flow of hydraulic fluid supplied to a swing motor; a loading side passage to which the bucket spool, the arm spool, the boom spool, and the swing spool are connected, and a traveling side passage to which the first traveling spool and the second traveling spool are connected; the second spool group including a valve block through which the spools of the first spool group are inserted in parallel to each other, a regeneration spool that controls the flow of hydraulic fluid supplied from the rod side port to the head side port of the arm cylinder, and a loading / unloading priority spool that controls the flow rate of hydraulic fluid flowing in the travel side passage to preferentially flow hydraulic fluid to the loading side passage, and the second spool group includes each spool inserted into the valve block so as to be parallel to each other with each spool of the first spool group, and the spools of the first spool group are arranged in a row in a predetermined direction in the valve block, and the spools of the second spool group are arranged in a row in the predetermined direction in the valve block and in a row different from each other with respect to the spools of the first spool group.

[0062] According to the above aspect, the spools of the drive system that drive the actuators, i.e., the cylinders and the motors, are arranged in a row, which makes it easy to form the passages. Also, the spools of the auxiliary systems other than the drive system spools are arranged in a row next to the row of the drive system spools, which makes it possible to form the multi-control valve in a compact form. Therefore, it is possible to improve the ease of installation in the equipment.

[0063] In a second aspect, the multi-control valve is the multi-control valve of the first aspect, wherein the loading priority spool can be positioned in an unloaded position and a priority position, and in the unloaded position, the hydraulic fluid flowing through the loading side passage is discharged, and in the priority position, the hydraulic fluid is preferentially allowed to flow through the loading side passage.

[0064] According to the above aspect, the loading priority spool can be moved to an unloading position and a priority position. In addition, the loading priority spool discharges hydraulic fluid flowing through the loading side passage when in the unloading position. In addition, the loading priority spool preferentially causes hydraulic fluid to flow through the loading side passage when in the priority position. Therefore, the loading priority spool has an unloading function and a loading priority function. Therefore, the unloading spool can be omitted in the multi-control valve. Therefore, the number of parts in the multi-control valve can be reduced.

[0065] In a third aspect, the multi-control valve is the multi-control valve of the first or second aspect, wherein the first traveling spool and the second traveling spool are arranged apart from each other in a predetermined direction, and the loading priority spool is arranged between the first traveling spool and the second traveling spool when viewed in the row direction in which the first spool group and the second spool group are arranged.

[0066] According to the above aspect, the priority spool is disposed between the first traveling spool and the second traveling spool in the row direction. Therefore, the difference in the length of the passage from the priority spool to each traveling spool can be reduced. That is, the difference in the pressure loss of the passage from the priority spool to each traveling spool can be reduced.

[0067] In a fourth aspect, in the multi-control valve of any one of the first to third aspects, the valve block includes a pump port, and the pump port is connected to the loading-side passage.

[0068] According to the above aspect, the pump port is connected to the cargo-side passage. Therefore, the length of the passage from the pump port to each spool of the cargo-side system can be reduced. This makes it possible to suppress pressure loss in the passage from the pump port to each spool of the cargo-side system.

[0069] In a fifth aspect, in the multi-control valve of any one of the first to fourth aspects, the travel-side passage is connected to the loading-side passage via the loading priority spool.

[0070] According to the above aspect, the travel-side passage is connected to the loading-side passage via the loading priority spool, so that a passage connecting the pump port and the loading-side passage can be omitted, thereby reducing the number of passages formed in the valve block.

[0071] A multi-control valve in a sixth aspect is the multi-control valve of any one of the first to fifth aspects, wherein the loading side passage and the travelling side passage are formed between the first spool group and the second spool group in the column direction in which the first spool group and the second spool group of the valve block are arranged.

[0072] According to the above aspect, the loading-side passage and the traveling-side passage are formed in the valve block between the first spool group and the second spool group in the row direction. Therefore, the passages connecting the loading-side passage and the traveling-side passage to each spool of the first spool group and the second spool group can be formed to be short. Also, since the loading-side passage and the traveling-side passage are formed between the first spool group and the second spool group in the row direction, the space on both sides of the valve block in the row direction can be effectively used.

[0073] A seventh aspect of the multi-control valve is the multi-control valve of the sixth aspect, wherein the valve block is formed with a communication passage that communicates the first traveling motor and the second traveling motor when hydraulic fluid is supplied to the first traveling motor and the second traveling motor, and the communication passage is formed between the first spool group and the second spool group in the column direction in which the first spool group and the second spool group are lined up in the valve block.

[0074] According to the above aspect, the communication passage is formed between the first spool group and the second spool group in the row direction in which the first spool group and the second spool group are arranged in the valve block. Therefore, the communication passage can be formed near the first traveling spool and the second traveling spool, so the length of the communication passage can be shortened. Also, since the communication passage is formed between the first spool group and the second spool group, the space on both sides of the row direction of the valve block can be effectively utilized. Furthermore, since the communication passage does not cross over the passages included in the first spool group and the second spool group, the effect of a change in passage pressure loss when another spool is operated can be suppressed. [Explanation of symbols]

[0075] 1. Multi-control valve 2 Bucket Cylinder 3 Arm Cylinder 3a Head side port 3b Rod side port 4 Boom cylinder 5. First traction motor 6. Second traction motor 7 Swivel motor 8 Actuators 11 Valve block 12 First spool group 13 Second spool group 14A solenoid valve group 14a~14r Solenoid valve 21 First running spool 22 Second running spool 23 Bucket spool 24 Arm Spool 25 Boom spool 26 Swivel spool 27 Option spool 28 Priority spool for loading and unloading 29 Arm Regeneration Spool (Regeneration Spool) 32 Cargo handling aisle 33 Traveling Side Passage 34 Communication path 35 Pump port

Claims

1. a first spool group including a bucket spool that controls the flow of hydraulic fluid supplied to the bucket cylinder, an arm spool that controls the flow of hydraulic fluid supplied to the arm cylinder, a boom spool that controls the flow of hydraulic fluid supplied to the boom cylinder, a first traveling spool that controls the flow of hydraulic fluid supplied to the first traveling motor, a second traveling spool that controls the flow of hydraulic fluid supplied to the second traveling motor, and a swing spool that controls the flow of hydraulic fluid supplied to the swing motor; a valve block in which a loading-side passage to which the bucket spool, the arm spool, the boom spool, and the swing spool are connected, and a traveling-side passage to which the first traveling spool and the second traveling spool are connected are formed, and through which the spools of the first spool group are inserted in parallel to each other; a second spool group including a regeneration spool that controls a flow of hydraulic fluid supplied from a rod side port to a head side port of the arm cylinder, and a loading / unloading priority spool that controls a flow rate of hydraulic fluid flowing through the travel side passage to preferentially flow hydraulic fluid to the loading side passage, wherein each spool of the second spool group is inserted into the valve block so as to be parallel to each spool of the first spool group, the spools of the first spool group are arranged in a row in a predetermined direction in the valve block, a multi-control valve, wherein each spool of the second spool group is arranged in a row in a predetermined direction in the valve block and in a row different from each other from each spool of the first spool group.

2. 2. The multi-control valve according to claim 1, wherein the cargo-loading priority spool can be positioned at an unloaded position and a priority position, and in the unloaded position, the spool discharges hydraulic fluid flowing through the cargo-loading side passage, and in the priority position, the spool allows hydraulic fluid to flow preferentially through the cargo-loading side passage.

3. The first traveling spool and the second traveling spool are disposed apart from each other in a predetermined direction, 2. The multi-control valve according to claim 1, wherein the loading priority spool is disposed between the first traveling spool and the second traveling spool as viewed in a row direction in which the first spool group and the second spool group are arranged.

4. the valve block includes a pump port; 2. The multi-control valve according to claim 1, wherein the pump port is connected to the loading-side passage.

5. 2. The multi-control valve according to claim 1, wherein the travel-side passage is connected to the loading-side passage via the loading priority spool.

6. 2. The multi-control valve according to claim 1, wherein the loading-side passage and the travel-side passage are formed between the first spool group and the second spool group in a column direction in which the first spool group and the second spool group of the valve block are aligned.

7. a communication passage that communicates between the first traveling motor and the second traveling motor when hydraulic fluid is supplied to the first traveling motor and the second traveling motor is formed in the valve block; 7. The multi-control valve according to claim 6, wherein the communication passage is formed between the first spool group and the second spool group in a column direction in which the first spool group and the second spool group are arranged in the valve block.

Images